JP5999050B2 - Ejector refrigeration cycle and ejector - Google Patents

Description

  The present invention relates to an ejector that decompresses a fluid and sucks the fluid by a suction action of a jet fluid ejected at a high speed, and an ejector refrigeration cycle that includes an ejector as a refrigerant decompression unit.

  2. Description of the Related Art Conventionally, an ejector refrigeration cycle that is a vapor compression refrigeration cycle including an ejector as refrigerant decompression means is known.

  For example, Patent Document 1 includes an accumulator that is a low-pressure side gas-liquid separation unit that separates gas-liquid refrigerant flowing out from an ejector and stores excess liquid-phase refrigerant, and further depressurizes the liquid-phase refrigerant separated by the accumulator. An ejector-type refrigeration cycle is disclosed in which the gas-phase refrigerant separated by the accumulator is sucked into the compressor while flowing into the evaporator.

  In the ejector-type refrigeration cycle of Patent Document 1, the refrigerant on the downstream side of the evaporator is sucked from the refrigerant suction port of the ejector by the suction action of the high-speed jet refrigerant injected from the nozzle portion of the ejector, and the ejector booster ( In the diffuser part), the mixed refrigerant of the injected refrigerant and the suction refrigerant is pressurized and flows into the accumulator.

  As a result, in the ejector refrigeration cycle of Patent Document 1, the refrigerant pressure in the accumulator can be made higher than the refrigerant evaporation pressure in the evaporator, and the refrigerant evaporation pressure in the evaporator and the suction refrigerant pressure in the compressor are substantially equal. Compared to the normal refrigeration cycle apparatus, the power consumption of the compressor can be reduced and the coefficient of performance (COP) of the cycle can be improved.

JP 2006-118727 A

  By the way, a refrigerant of a general vapor compression refrigeration cycle including an ejector refrigeration cycle is mixed with a refrigeration oil that is an oil for lubricating the compressor, and this type of refrigeration oil includes a liquid-phase refrigerant. Those having compatibility are adopted.

  For this reason, in the configuration in which the gas-phase refrigerant separated by the accumulator is sucked into the compressor as in the ejector refrigeration cycle of Patent Document 1, the refrigeration oil becomes difficult to be supplied to the compressor, and the compressor lubrication is performed. A shortage tends to adversely affect the durable life of the compressor. Furthermore, if the concentration of the refrigeration oil in the liquid phase refrigerant separated by the accumulator rises and the liquid phase refrigerant with a high concentration of refrigeration oil flows into the evaporator, the refrigeration oil stays in the evaporator and evaporates. The heat exchange performance of the vessel is likely to deteriorate.

  Therefore, in general, in a refrigeration cycle equipped with an accumulator, a part of the liquid phase refrigerant separated by the accumulator and having a relatively high concentration of refrigeration oil is returned to the gas phase refrigerant sucked into the compressor. In addition to suppressing lubrication shortage of the compressor, the amount of refrigerating machine oil flowing into the evaporator is reduced to prevent the refrigerating machine oil from staying in the evaporator.

  Furthermore, in order to study a means for efficiently returning the refrigeration oil in the liquid-phase refrigerant separated by the accumulator to the gas-phase refrigerant sucked into the compressor, in the refrigeration cycle including the accumulator, The relationship between the concentration of refrigerating machine oil in the liquid-phase refrigerant flowing into the evaporator and the cooling capacity of the cooling target fluid in the evaporator was investigated.

  As a result, it was confirmed that as the concentration of refrigeration oil in the liquid-phase refrigerant flowing into the evaporator increases, the amount of refrigeration oil remaining in the evaporator increases and the cooling capacity of the evaporator decreases. In addition, if the concentration of the refrigeration oil in the liquid-phase refrigerant flowing into the evaporator is lower than the predetermined concentration, the cooling capacity of the evaporator decreases with a decrease in the concentration of the refrigeration oil. It was confirmed.

  Then, when the present inventors investigated the reason, when the density | concentration of the refrigerating machine oil in the refrigerant | coolant which flows into an evaporator has become a suitable density | concentration, the particle | grains (oil droplet) of the refrigerating machine oil melt | dissolved in the refrigerant | coolant It has been found that can perform the function corresponding to the boiling nuclei of the refrigerant, and promote the evaporation of the liquid phase refrigerant in the evaporator to improve the cooling capacity in the evaporator.

  This means that the cooling capacity in the evaporator has a maximum value (peak value) depending on the concentration of the refrigerating machine oil. That is, the cooling capacity in the evaporator can be brought close to the maximum value by adjusting the concentration of the refrigerating machine oil in the liquid-phase refrigerant flowing into the evaporator to an appropriate value.

  An object of the present invention is to provide an ejector-type refrigeration cycle configured to be capable of adjusting the concentration of refrigerating machine oil in a liquid-phase refrigerant that flows into an evaporator.

  Further, the present invention is applied to a vapor compression refrigeration cycle and provides an ejector integrated with a gas-liquid separation means configured to be capable of adjusting the concentration of refrigeration oil in a liquid phase refrigerant flowing out to the outside. The purpose.

  The present invention has been devised to achieve the above object. In the invention described in claim 1, a compressor (11) that compresses and discharges refrigerant mixed with refrigerating machine oil, and a compressor ( 11) The refrigerant suction port by the suction action of the high-speed jet refrigerant jetted from the radiator (12) that radiates the refrigerant discharged from 11) and the nozzle portion (21) that depressurizes the refrigerant that flows out of the radiator (12) An ejector (20) for sucking the refrigerant from (22a) and increasing the pressure of the mixed refrigerant of the injected refrigerant and the sucked refrigerant sucked from the refrigerant suction port (22a) by the boosting section (22b), and flowing out from the ejector (20) The upstream gas that separates the gas-liquid from the refrigerant and causes the separated refrigerant to flow out from the liquid-phase refrigerant outlet (14a) without accumulating the separated liquid-phase refrigerant and also causes the remaining refrigerant to flow out from the mixed-phase refrigerant outlet (14b). Liquid separation means ( 4), the evaporator (16) that evaporates the liquid-phase refrigerant that has flowed out from the liquid-phase refrigerant outlet (14a) and flows out to the refrigerant suction port (22a) side, and the refrigerant that has flowed out from the mixed-phase refrigerant outlet (14b) The downstream gas that separates the gas-liquid of the refrigerant in which the gas-phase refrigerant and the liquid-phase refrigerant are mixed, stores the separated liquid-phase refrigerant, and causes the separated gas-phase refrigerant to flow out to the suction port side of the compressor (11). Ejector refrigeration comprising liquid separation means (17) and refrigeration oil concentration adjusting means (22c, 23, 14c, 23a) for adjusting the concentration of refrigeration oil in the liquid phase refrigerant flowing out from the liquid phase refrigerant outlet (14a). It features a cycle.

  According to this, since the refrigerating machine oil concentration adjusting means (22c, 23, 14c, 23a) is provided, the liquid-phase refrigerant outlet (14a) of the upstream gas-liquid separation means (14) to the evaporator (16). The concentration of the refrigerating machine oil in the inflowing liquid phase refrigerant can be adjusted to a desired concentration. Therefore, the cooling capacity of the cooling target fluid in the evaporator (16) can be brought close to the maximum value.

  Further, in the upstream gas-liquid separation means (14), the separated liquid-phase refrigerant is allowed to flow out from the liquid-phase refrigerant outlet (14a) without accumulating. Therefore, as in the case where the upstream gas-liquid separation means (14) having a liquid storage function is adopted, the evaporator is used by the refrigerating machine oil dissolved in the liquid phase refrigerant stored in the upstream gas-liquid separation means (14). The concentration of the refrigerating machine oil in the liquid refrigerant flowing into (16) does not change.

  Further, since the downstream gas-liquid separation means (17) has a function of storing the separated liquid-phase refrigerant, the gas-phase refrigerant can be reliably supplied to the suction port side of the compressor (11). The problem of liquid compression of the compressor (11) can be avoided. Furthermore, by returning a part of the liquid phase refrigerant in which the refrigerating machine oil stored in the downstream gas-liquid separation means (17) is dissolved to the gas phase refrigerant on the suction port side of the compressor (11), the compressor (11 ) Can be suppressed.

  The cooling ability of the cooling target fluid in the evaporator (16) can be defined as the ability to cool the cooling target fluid at a desired flow rate to a desired temperature.

  Therefore, the cooling capacity is improved as the refrigerant evaporation temperature in the evaporator (16) is lowered, and the refrigeration capacity that the refrigerant exhibits in the evaporator (16) (from the enthalpy of the outlet side refrigerant of the evaporator (16)). The value obtained by subtracting the enthalpy of the refrigerant on the inlet side increases as the refrigerant flow increases, and further increases as the flow rate of refrigerant flowing into the evaporator (16) increases.

  More specifically, the refrigerating machine oil concentration adjusting means is provided by a refrigerating machine oil bypass passage (23) for guiding the refrigerating machine oil in the booster (22b) of the ejector (20) to the downstream side of the refrigerant flow of the mixed phase refrigerant outlet (14b). It may be configured.

  Further, as the upstream side gas-liquid separation means (14), a centrifugal separation type means for separating the gas-liquid of the refrigerant by the action of centrifugal force generated by turning the refrigerant flowing into the inside is adopted, and the refrigerating machine oil concentration adjusting means May be constituted by a refrigerating machine oil bypass passage (23a) that guides the refrigerating machine oil in the upstream gas-liquid separation means (14) to the downstream side of the refrigerant flow of the mixed phase refrigerant outlet (14b).

The invention according to claim 5 is an ejector applied to a vapor compression refrigeration cycle apparatus (10) for circulating a refrigerant mixed with refrigeration oil,
The decompression space (30b) that decompresses the refrigerant, the suction passage (13b) that communicates with the downstream side of the refrigerant flow in the decompression space (30b) and sucks the coolant from the outside, and the decompression space (30b) A body (30) formed with a pressure increasing space (30e) into which the injected refrigerant and the suction refrigerant sucked from the suction passage (13b) flow, and at least a part of the inside of the pressure reducing space (30b) and the pressure increasing space A passage forming member (35) disposed in the space (30e) and having a conical shape whose cross-sectional area expands with distance from the decompression space (30b),
The refrigerant passage formed between the inner peripheral surface of the body (30) forming the decompression space (30b) and the outer peripheral surface of the passage forming member (35) serves as a nozzle that decompresses and injects the refrigerant. The functioning nozzle passage (13a) is a refrigerant passage formed between the inner peripheral surface of the body (30) forming the pressurizing space (30e) and the outer peripheral surface of the passage forming member (35). A diffuser passage (13c) that functions as a diffuser that converts the kinetic energy of the mixed refrigerant of the injection refrigerant and the suction refrigerant into pressure energy,
Further, the gas (liquid) of the refrigerant flowing out from the diffuser passage (13c) is separated into the body (30), and the separated liquid phase refrigerant is discharged outside from the liquid phase refrigerant outlet (31c) without accumulating. The refrigerant gas in the upstream gas-liquid separation space (30f) through which the remaining refrigerant flows out from the mixed-phase refrigerant outlet (34d), the refrigerating machine oil in the diffuser passage (13c), and the refrigerating machine oil in the upstream gas-liquid separation space (30f) Refrigerating machine oil bypass passage (34c, which adjusts the concentration of the refrigerating machine oil in the liquid refrigerant flowing out from the liquid refrigerant outlet (31c) by guiding at least one of them to the downstream side of the mixed refrigerant outlet (34d). 35b) is formed.

  According to this, since the refrigerating machine oil bypass passages (34c, 35b) are formed, the concentration of the refrigerating machine oil in the liquid phase refrigerant flowing out from the liquid phase refrigerant outlet (31c) is adjusted to a desired concentration. be able to. That is, it is possible to provide a gas-liquid separation unit integrated ejector configured to be capable of adjusting the concentration of refrigeration oil in the liquid-phase refrigerant that flows out to the outside.

  Therefore, when applied to the vapor compression refrigeration cycle, the cooling capacity of the cooling target fluid in the evaporator is maximized by flowing the liquid refrigerant flowing out of the liquid refrigerant outlet (31c) into the evaporator. You can get closer.

  Furthermore, in the upstream gas-liquid separation space (30f), the separated liquid-phase refrigerant is allowed to flow out from the liquid-phase refrigerant outlet (31c) without accumulating. Accordingly, the refrigerant flows out to the outside by the refrigerating machine oil dissolved in the liquid phase refrigerant stored in the upstream gas-liquid separation space (30f) as in the case where the upstream gas-liquid separation space (30f) has a liquid storage function. The concentration of the refrigeration oil in the liquid phase refrigerant to be changed does not change.

  In addition, in this claim, the passage forming member (35) is not limited to one that is formed only from a shape whose cross-sectional area expands strictly as it is separated from the decompression space (30b). The shape of the diffuser passage (13c) is made to expand outward as it moves away from the decompression space (30b) by including a shape in which the cross-sectional area increases as it moves away from the decompression space (30b). Including those that can.

Further, “conically formed” is not limited to the meaning that the passage forming member (35) is formed in a complete conical shape, and includes a shape close to a cone or a portion of the cone. It also includes the meaning of being formed. Specifically, the shape in which the axial cross-sectional shape is not limited to an isosceles triangle, the shape in which the two sides sandwiching the apex are convex on the inner peripheral side, the shape in which the two sides sandwiching the apex are convex on the outer peripheral side, In addition, it also means that the cross-sectional shape is a semicircular shape, etc.Note that the reference numerals in parentheses of each means described in this column and in the claims correspond to the specific means described in the embodiments described later. It shows the relationship.

It is a whole block diagram of the ejector-type refrigerating cycle of 1st Embodiment. It is a graph which shows the relationship between the density | concentration of the refrigerating machine oil in the refrigerant | coolant which flows in into an evaporator, and the heat exchange performance in an evaporator. It is a whole block diagram of the ejector type refrigerating cycle of 2nd Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 3rd Embodiment. It is an axial sectional view of an ejector of a 3rd embodiment. It is typical sectional drawing for demonstrating the function of each refrigerant path of the ejector of 3rd Embodiment. It is an axial sectional view of an ejector according to a fourth embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 5th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 6th Embodiment.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. As shown in the overall configuration diagram of FIG. 1, the ejector 20 of the present embodiment is applied to a vapor compression refrigeration cycle apparatus including an ejector as refrigerant decompression means, that is, an ejector refrigeration cycle 10. Furthermore, this ejector type refrigeration cycle 10 is applied to a vehicle air conditioner, and fulfills a function of cooling the blown air blown into the vehicle interior, which is the air-conditioning target space.

  The ejector refrigeration cycle 10 employs an HFC refrigerant (specifically, R134a) as the refrigerant, and constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the refrigerant critical pressure. . Of course, an HFO refrigerant (specifically, R1234yf) or the like may be adopted as the refrigerant.

  Further, the refrigerant is mixed with refrigerating machine oil (oil) for lubricating the compressor 11. As this refrigerating machine oil, PAG oil (polyalkylene glycol oil) having compatibility with the liquid phase refrigerant is employed. In addition, the density of this refrigerating machine oil is smaller than the density of a liquid phase refrigerant. A part of the refrigeration oil circulates in the cycle together with the refrigerant.

  In the ejector-type refrigeration cycle 10, the compressor 11 sucks the refrigerant and discharges it until it becomes high-pressure refrigerant. Specifically, the compressor 11 of the present embodiment is an electric compressor configured by housing a fixed capacity type compression mechanism and an electric motor that drives the compression mechanism in one housing.

  As this compression mechanism, various compression mechanisms such as a scroll-type compression mechanism and a vane-type compression mechanism can be employed. Further, the operation (rotation speed) of the electric motor is controlled by a control signal output from a control device to be described later, and either an AC motor or a DC motor may be adopted.

  The compressor 11 may be an engine-driven compressor that is driven by a rotational driving force transmitted from a vehicle travel engine via a pulley, a belt, or the like. As this type of engine-driven compressor, a variable displacement compressor that can adjust the refrigerant discharge capacity by changing the discharge capacity, or adjusting the refrigerant discharge capacity by changing the operating rate of the compressor by intermittently connecting the electromagnetic clutch. A fixed capacity compressor can be employed.

  The refrigerant inlet side of the condenser 12 a of the radiator 12 is connected to the discharge port of the compressor 11. The radiator 12 is a heat exchanger for heat radiation that radiates and cools the high-pressure refrigerant by exchanging heat between the high-pressure refrigerant discharged from the compressor 11 and outside air (outside air) blown by the cooling fan 12d. .

  More specifically, the radiator 12 is a condensing unit that exchanges heat between the high-pressure gas-phase refrigerant discharged from the compressor 11 and the outside air blown from the cooling fan 12d to radiate and condense the high-pressure gas-phase refrigerant. 12a, a receiver unit 12b which is a high-pressure side gas-liquid separation unit that separates the gas-liquid refrigerant flowing out of the condensing unit 12a and stores excess liquid-phase refrigerant, and the liquid-phase refrigerant flowing out of the receiver unit 12b and the cooling fan 12d It is a so-called subcool type condenser configured to have a supercooling section 12c that exchanges heat with the outside air and supercools the liquid refrigerant.

  Further, the cooling fan 12d is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the control device.

  The refrigerant outlet of the supercooling portion 12c of the radiator 12 is connected to the inlet side of the high-pressure refrigerant passage 18 constituting the internal heat exchange means. The high-pressure refrigerant passage 18 is formed of a spiral metal pipe and is disposed inside a low-pressure liquid-phase refrigerant stored in a downstream gas-liquid separator 17 described later. Therefore, the refrigerant flowing out of the radiator 12 exchanges heat with the low-pressure liquid-phase refrigerant stored in the downstream gas-liquid separator 17 when flowing through the high-pressure refrigerant passage 18.

  The outlet of the high-pressure refrigerant passage 18 is connected to the refrigerant inlet 21 a side of the nozzle portion 21 of the ejector 20. The ejector 20 functions as a refrigerant depressurizing unit that depressurizes the supercooled high-pressure liquid-phase refrigerant that has flowed out of the high-pressure refrigerant passage 18 and flows it downstream, and by the suction action of the refrigerant flow injected at a high speed. It functions as a refrigerant circulating means (refrigerant transporting means) for sucking (transporting) and circulating the refrigerant flowing out of the evaporator 16 described later.

  More specifically, the ejector 20 includes a nozzle part 21 and a body part 22. The nozzle portion 21 is formed of a substantially cylindrical metal (for example, a stainless alloy) that gradually tapers in the refrigerant flow direction, and the refrigerant is passed through the refrigerant passage (throttle passage) formed therein. It is expanded under reduced pressure in an isentropic manner.

  The refrigerant passage formed inside the nozzle portion 21 has a throat portion (minimum passage area portion) with the smallest refrigerant passage area, and a point where the refrigerant passage area gradually decreases from the refrigerant inlet 21a side toward the throat portion. A divergent part in which the area of the refrigerant passage gradually increases toward the refrigerant injection port for injecting the refrigerant from the details and the throat is provided. That is, the nozzle part 21 of this embodiment is configured as a Laval nozzle.

  Moreover, in this embodiment, what was set so that the flow rate of the injection refrigerant | coolant injected from a refrigerant | coolant injection port may become more than a sound speed at the time of the normal driving | operation of the ejector-type refrigeration cycle 10 as the nozzle part 21 is employ | adopted. Of course, you may comprise the nozzle part 21 with a tapered nozzle.

  The body portion 22 is formed of a substantially cylindrical metal (for example, aluminum) or resin, and functions as a fixing member that supports and fixes the nozzle portion 21 therein and forms an outer shell of the ejector 20. . More specifically, the nozzle portion 21 is fixed by press-fitting so as to be housed inside the longitudinal end of the body portion 22. Therefore, the refrigerant does not leak from the fixed portion (press-fit portion) between the nozzle portion 21 and the body portion 22.

  In addition, a refrigerant suction port 22 a provided so as to penetrate the inside and outside of the outer peripheral surface of the body portion 22 and communicate with the refrigerant injection port of the nozzle portion 21 is provided in a portion corresponding to the outer peripheral side of the nozzle portion 21. Is formed. The refrigerant suction port 22 a is a through hole that sucks the refrigerant that has flowed out of the evaporator 16, which will be described later, into the ejector 20 by the suction action of the injection refrigerant that is injected from the nozzle portion 21.

  Further, inside the body portion 22, a suction passage that leads the suctioned refrigerant sucked from the refrigerant suction port 22 a to the refrigerant injection port side of the nozzle portion 21, and the refrigerant suction port 22 a to the inside of the ejector 20 through the suction passage. A diffuser portion 22b is formed as a pressure increasing portion for mixing and increasing the pressure of the sucked refrigerant and the injected refrigerant.

  The suction passage is formed in a space between the outer peripheral side around the tapered tip end portion of the nozzle portion 21 and the inner peripheral side of the body portion 22, and the refrigerant passage area of the suction passage is directed toward the refrigerant flow direction. It is gradually shrinking. Thereby, the flow velocity of the suction refrigerant flowing through the suction passage is gradually increased, and the energy loss (mixing loss) when the suction refrigerant and the injection refrigerant are mixed in the diffuser portion 22b is reduced.

  The diffuser portion 22b is arranged so as to be continuous with the outlet of the suction passage, and is formed so that the refrigerant passage area gradually increases. Thereby, while mixing the injected refrigerant and the suction refrigerant, the function of decelerating the flow rate and increasing the pressure of the mixed refrigerant of the injection refrigerant and the suction refrigerant, that is, the function of converting the velocity energy of the mixed refrigerant into pressure energy Fulfill.

  More specifically, the cross-sectional shape in the axial cross section of the inner peripheral wall surface of the body portion 22 forming the diffuser portion 22b of the present embodiment is formed by combining a plurality of curves. And since the degree of spread of the refrigerant passage cross-sectional area of the diffuser portion 22b gradually increases in the refrigerant flow direction and then decreases again, the pressure of the refrigerant can be increased isentropically.

  Furthermore, the ejector 20 of the present embodiment is connected to a refrigerator oil bypass passage 23 that guides the refrigerator oil in the diffuser portion 22b to the downstream side of the refrigerant flow at the mixed-phase refrigerant outlet 14b of the upstream gas-liquid separator 14 described later. ing. The refrigerating machine oil in the diffuser section 22b includes both refrigerating machine oil dissolved in the refrigerant flowing through the diffuser section 22b and refrigerating machine oil precipitated from the refrigerant flowing through the diffuser section 22b.

  More specifically, a small-diameter hole that penetrates the inside and outside of the body portion 22 of the present embodiment is a portion that forms the diffuser portion 22b and is closer to the outlet side than the inlet side of the diffuser portion 22b. 22c is formed.

  The refrigerating machine oil bypass passage 23 is constituted by a refrigerant pipe connecting the small-diameter hole 22c and the downstream gas-liquid separator 17, and the refrigerating machine oil or refrigerating machine oil flowing out from the small-diameter hole 22c is melted at a high concentration. The refrigerant is guided into the downstream gas-liquid separator 17. The refrigerating machine oil bypass passage 23 is formed by a pipe having a small diameter with respect to other refrigerant pipes, and can be specifically constituted by a capillary tube or the like.

  The refrigerant outlet of the diffuser portion 22b of the ejector 20 is connected to the refrigerant inlet side of the upstream gas-liquid separator 14 serving as the upstream gas-liquid separator. The upstream-side gas-liquid separator 14 is formed of a hollow cylindrical sealed container, separates the gas-liquid of the refrigerant flowing into the inside, and stores the separated liquid-phase refrigerant without storing the separated liquid-phase refrigerant 14a. The remaining refrigerant that has not been allowed to flow out from the liquid-phase refrigerant outlet 14a is allowed to flow out from the mixed-phase refrigerant outlet 14b.

  More specifically, in the present embodiment, as the upstream gas-liquid separator 14, the refrigerant gas-liquid is separated by the action of centrifugal force generated by swirling the refrigerant flowing into the internal space of the cylindrical main body. A centrifugal separator is used. Furthermore, the internal volume of the main body portion of the upstream gas-liquid separator 14 is the amount of refrigerant necessary for the cycle to exert its maximum capacity from the amount of refrigerant contained when the amount of refrigerant enclosed in the cycle is converted to the liquid phase. Is set to be smaller than the surplus refrigerant volume obtained by subtracting the required maximum refrigerant volume when converted into a liquid phase.

  For this reason, the internal volume of the upstream gas-liquid separator 14 of the present embodiment is such that even if a load fluctuation occurs in the cycle and the refrigerant circulation flow rate circulating in the cycle fluctuates, the surplus refrigerant cannot be substantially accumulated. The volume is Accordingly, the liquid-phase refrigerant outlet 14a functions exclusively as a refrigerant outlet for allowing the liquid-phase refrigerant to flow out, and the mixed-phase refrigerant outlet 14b is a refrigerant for causing the gas-phase refrigerant or a mixture of the gas-phase refrigerant and the liquid-phase refrigerant to flow out. Functions as an outlet.

  The liquid refrigerant outlet 14a of the upstream gas-liquid separator 14 is formed on the bottom surface of the cylindrical main body. Further, the mixed-phase refrigerant outlet 14b of the upstream side gas-liquid separator 14 is arranged coaxially in the main body part, and protrudes upward from the lower side of the main body part above the liquid level of the liquid phase refrigerant in the main body part. It is formed in the upper end part of the cylindrical pipe member extended in this.

  The refrigerant inlet side of the evaporator 16 is connected to the liquid-phase refrigerant outlet 14a of the upstream gas-liquid separator 14 via a fixed throttle 15 as a decompression means. The fixed throttle 15 is a decompression unit that decompresses the liquid-phase refrigerant that has flowed out of the upstream gas-liquid separator 14, and specifically, an orifice, a capillary tube, a nozzle, or the like can be employed.

  The evaporator 16 performs heat exchange between the low-pressure refrigerant decompressed by the fixed throttle 15 and the blown air blown from the blower fan 16a toward the vehicle interior, thereby evaporating the low-pressure refrigerant and exerting an endothermic effect. Heat exchanger. The blower fan 16a is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the control device. The refrigerant outlet of the evaporator 16 is connected to the refrigerant suction port 22 a side of the ejector 20.

  On the other hand, a refrigerant inlet side of a downstream gas-liquid separator 17 as a downstream gas-liquid separator (accumulator) is connected to the mixed-phase refrigerant outlet 14b side of the upstream gas-liquid separator 14. The downstream gas-liquid separator 17 is formed of a hollow cylindrical airtight container, separates the gas-liquid of the refrigerant flowing into the interior, stores the separated liquid-phase refrigerant, and separates the separated gas-phase refrigerant. Is discharged from the gas-phase refrigerant outlet to the suction port side of the compressor 11.

  In addition, on the lower side of the downstream gas-liquid separator 17 (the side on which the liquid-phase refrigerant is stored), a part of the stored liquid-phase refrigerant is guided to the suction port side of the compressor 11 to be converted into the liquid-phase refrigerant. An oil return passage 17a for returning the melted refrigeration oil to the gas-phase refrigerant on the suction port side of the compressor 11 is connected. Similar to the refrigerator oil bypass passage 23, the oil return passage 17a is formed by a pipe having a small diameter with respect to other refrigerant pipes.

  Next, a control device (not shown) includes a known microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof. This control device performs various calculations and processes based on the control program stored in the ROM, and controls the operations of the above-described various electric actuators 11, 12d, 16a and the like.

  The control device detects an inside air temperature sensor that detects the temperature inside the vehicle, an outside air temperature sensor that detects the outside air temperature, a solar radiation sensor that detects the amount of solar radiation inside the vehicle, and detects the temperature of the air blown from the evaporator 16 (temperature of the evaporator). A group of sensors for air conditioning control, such as an evaporator temperature sensor, an outlet side temperature sensor that detects the temperature of the radiator 12 outlet-side refrigerant, and an outlet-side pressure sensor that detects the pressure of the radiator 12 outlet-side refrigerant. The detection value of the sensor group is input.

  Furthermore, an operation panel (not shown) disposed near the instrument panel in the front part of the vehicle interior is connected to the input side of the control device, and operation signals from various operation switches provided on the operation panel are input to the control device. The As various operation switches provided on the operation panel, there are provided an air conditioning operation switch for requesting air conditioning in the vehicle interior, a vehicle interior temperature setting switch for setting the vehicle interior temperature, and the like.

  Note that the control device of the present embodiment is configured integrally with control means for controlling the operation of various control target devices connected to the output side of the control device. The configuration (hardware and software) for controlling the operation constitutes the control means of each control target device. For example, in the present embodiment, the configuration (hardware and software) that controls the operation of the compressor 11 constitutes the discharge capacity control means.

  Next, the operation of this embodiment in the above configuration will be described. First, when the air conditioning operation switch on the operation panel is turned on (ON), the control device operates the compressor 11, the cooling fan 12d, the blower fan 16a, and the like. Thereby, the compressor 11 sucks the refrigerant, compresses it, and discharges it.

  The high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the condensing part 12a of the radiator 12, exchanges heat with the outside air blown from the cooling fan 12d, dissipates heat, and condenses. The refrigerant that has dissipated heat in the condensing unit 12a is gas-liquid separated in the receiver unit 12b. The liquid-phase refrigerant separated from the gas and liquid in the receiver unit 12b exchanges heat with the outside air blown from the cooling fan 12d in the supercooling unit 12c, and further dissipates heat to become a supercooled liquid-phase refrigerant.

  The supercooled liquid phase refrigerant that has flowed out of the supercooling portion 12 c of the radiator 12 flows into the high-pressure refrigerant passage 18 and exchanges heat with the liquid phase refrigerant stored in the downstream gas-liquid separator 17. Thereby, the supercooled liquid phase refrigerant flowing through the high-pressure refrigerant passage 18 further reduces enthalpy. On the other hand, the liquid-phase refrigerant in the downstream gas-liquid separator 17 absorbs heat from the supercooled liquid-phase refrigerant flowing through the high-pressure refrigerant passage 18 and evaporates by increasing the enthalpy.

  The refrigerant that has flowed out of the high-pressure refrigerant passage 18 flows into the nozzle portion 21 of the ejector 20 and is decompressed and injected in an isoenthalpy manner. The refrigerant flowing out of the evaporator 16 is sucked from the refrigerant suction port 22a of the ejector 20 by the suction action of the jet refrigerant. The suction refrigerant sucked from the refrigerant suction port 22a flows into the diffuser portion 22b of the ejector 20 together with the injection refrigerant.

  In the diffuser portion 22b, the kinetic energy of the refrigerant is converted into pressure energy by expanding the refrigerant passage area. As a result, the pressure of the mixed refrigerant rises while the injected refrigerant and the suction refrigerant are mixed. Further, in the present embodiment, the refrigerant in which the refrigeration oil is dissolved at a high concentration or the refrigeration oil deposited from the refrigerant flows into the downstream gas-liquid separator 17 through the small diameter hole 22c and the refrigeration oil bypass passage 23. .

  The refrigerant flowing out from the outlet portion of the diffuser portion 22b flows into the upstream gas-liquid separator 14 and is separated into gas and liquid. Here, as described above, the upstream gas-liquid separator 14 does not have a function of storing the separated liquid-phase refrigerant. Therefore, not only the separated liquid phase refrigerant flows out from the liquid phase refrigerant outlet 14a, but also the remaining liquid phase refrigerant that did not flow out from the liquid phase refrigerant outlet 14a among the separated liquid phase refrigerants was separated. It flows out of the mixed-phase refrigerant outlet 14b together with the gas-phase refrigerant.

  The liquid phase refrigerant flowing out from the liquid phase refrigerant outlet 14 a of the upstream side gas-liquid separator 14 is decompressed in an enthalpy manner by the fixed throttle 15 and flows into the evaporator 16. The refrigerant flowing into the evaporator 16 absorbs heat from the blown air blown from the blower fan 16a and evaporates. Thereby, the blowing air blown into the passenger compartment is cooled. Further, the refrigerant flowing out of the evaporator 16 is sucked from the refrigerant suction port 22a of the ejector 20.

  On the other hand, the refrigerant in which the gas-phase refrigerant and the liquid-phase refrigerant that have flowed out from the mixed-phase refrigerant outlet 14b of the upstream gas-liquid separator 14 are mixed flows into the downstream gas-liquid separator 17 and is gas-liquid separated. The liquid phase refrigerant separated by the downstream gas-liquid separator 17 is stored in the downstream gas-liquid separator 17, and the gas-phase refrigerant separated by the downstream gas-liquid separator 17 is sent to the compressor 11. Inhaled and compressed again.

  Further, in the present embodiment, a part of the liquid-phase refrigerant stored in the downstream gas-liquid separator 17 is sucked into the compressor 11 via the oil return passage 17 a connected to the downstream gas-liquid separator 17. To the side. Thereby, the refrigeration oil dissolved in the liquid phase refrigerant is returned to the gas phase refrigerant on the suction side of the compressor 11 and is sucked into the compressor 11 together with the gas phase refrigerant.

  The ejector refrigeration cycle 10 of the present embodiment operates as described above and can cool the blown air blown into the vehicle interior. Further, in the ejector refrigeration cycle 10, the refrigerant whose pressure has been increased by the diffuser portion 22b is sucked into the compressor 11 via the upstream gas-liquid separator 14 and the downstream gas-liquid separator 17, so that the compressor 11 driving power can be reduced and cycle efficiency (COP) can be improved.

  Further, since the ejector refrigeration cycle 10 of the present embodiment includes the refrigeration oil bypass passage 23, the refrigeration oil in the diffuser portion 22b can be easily guided into the downstream gas-liquid separator 17.

  To explain this in more detail, as described above, in the diffuser section 22b, the kinetic energy of the mixed refrigerant of the injected refrigerant and the suction refrigerant is converted into pressure energy, so the flow rate of the mixed refrigerant flowing through the diffuser section 22b is The refrigerant flow gradually decreases toward the downstream side. Further, in the diffuser portion 22b, the flow velocity of the refrigerant in the vicinity of the inner peripheral wall surface of the body portion 22 where the diffuser portion 22b is formed is reduced due to wall friction when the refrigerant flows.

  Accordingly, the flow velocity of the refrigerant is greatly reduced in the vicinity of the inner peripheral wall surface of the body portion 22 where the diffuser portion 22b is formed and near the outlet side of the diffuser portion 22b. For this reason, a liquid phase refrigerant tends to adhere to the inner peripheral wall surface of the body portion 22 that forms a portion closer to the outlet side than the inlet side of the diffuser portion 22b.

  Furthermore, since the refrigerating machine oil easily dissolves in the liquid phase refrigerant adhering to the inner peripheral wall surface due to a decrease in the flow velocity, the concentration of the refrigerating machine oil in the liquid phase refrigerant adhering to the inner peripheral wall surface increases. When the amount of the refrigerating machine oil dissolved in the liquid refrigerant adhering to the inner peripheral wall surface exceeds the solubility, the refrigerating machine oil is deposited on the inner peripheral wall surface of the body portion 22.

  Thereby, in this embodiment, the refrigerant | coolant which refrigeration oil or refrigerating machine oil melt | dissolved with high density | concentration can be discharged | emitted from the small diameter hole 22c formed in the body 22, Furthermore, refrigerating machine oil is passed through the refrigerating machine oil bypass channel 23. Alternatively, the refrigerant in which the refrigerating machine oil is dissolved at a high concentration can be easily introduced into the downstream gas-liquid separator 17.

  Then, the refrigeration oil in the diffuser part 22b is guided to the downstream gas-liquid separator 17 through the small-diameter hole 22c and the refrigeration oil bypass passage 23 in this way, and flows out from the diffuser part 22b to be separated from the upstream gas-liquid separation. The amount of refrigerating machine oil flowing into the vessel 14 is reduced.

  That is, in this embodiment, the small diameter hole 22c and the refrigerator oil bypass passage 23 are provided, whereby the amount of the refrigerator oil flowing into the upstream gas-liquid separator 14 is adjusted, and further, the upstream gas-liquid separator The concentration of the refrigerating machine oil in the liquid phase refrigerant flowing out from the 14 liquid phase refrigerant outlets 14a is adjusted. Therefore, the small diameter hole 22c and the refrigerating machine oil bypass 23 of the present embodiment constitute a refrigerating machine oil concentration adjusting means described in the claims.

  Here, the influence of the concentration of the refrigeration oil in the liquid phase refrigerant flowing out from the upstream gas-liquid separator 14 and flowing into the evaporator 16 on the cooling capacity of the evaporator 16 will be described. The cooling capacity in the evaporator 16 can be defined as an ability to cool the cooling target fluid (in this embodiment, blown air in the present embodiment) at a desired flow rate until the temperature reaches a desired temperature.

  In general, if the concentration of the refrigeration oil in the liquid refrigerant flowing into the evaporator 16 increases, the refrigeration oil may stay in the evaporator 16 and deteriorate the heat exchange performance of the evaporator 16. Are known.

  Therefore, the present inventors go to the evaporator 16 in order to study means for efficiently returning the refrigeration oil in the liquid refrigerant flowing into the evaporator 16 to the gas-phase refrigerant on the suction port side of the compressor 11. The relationship between the concentration of refrigeration oil in the inflowing liquid-phase refrigerant and the cooling capacity of the cooling target fluid in the evaporator 16 was investigated.

  As a result, as shown in the graph of FIG. 2, as the concentration of the refrigerating machine oil increases, the amount of the refrigerating machine oil staying in the evaporator 16 increases and the cooling capacity in the evaporator decreases. Not only was it confirmed, but when the concentration of the refrigerating machine oil was lower than the predetermined concentration, it was confirmed that the cooling capacity in the evaporator 16 would decrease as the concentration of the refrigerating machine oil decreased. .

  Then, when the present inventors investigated the reason, when the density | concentration of the refrigerating machine oil in the refrigerant | coolant which flows into the evaporator 16 has become a suitable density | concentration, the particle | grains (oil droplets) of the refrigerating oil dissolved in the refrigerant | coolant ) Has a function corresponding to the boiling nuclei of the refrigerant, and it has been found that the vaporization of the liquid-phase refrigerant in the evaporator 16 is promoted to improve the cooling capacity in the evaporator 16.

  This means that the cooling capacity in the evaporator 16 has a maximum value (peak value) depending on the concentration of the refrigerating machine oil. In other words, it means that the cooling capacity in the evaporator 16 can be brought close to the maximum value by adjusting the concentration of the refrigerating machine oil in the liquid-phase refrigerant that flows into the evaporator 16 to an appropriate value.

  Therefore, in the present embodiment, the inner diameter (refrigerant passage area) of the refrigerating machine oil bypass passage 23 constituting the refrigerating machine oil concentration adjusting means, the diameter of the small-diameter hole 22c, or the like is set to an appropriate value so as to flow into the evaporator 16. The concentration of the refrigerating machine oil in the liquid phase refrigerant can be adjusted to a desired value. And the density | concentration of the refrigerating machine oil in the liquid phase refrigerant | coolant which flows in into the evaporator 16 is adjusted so that the cooling capacity in the evaporator 16 may approach the maximum value.

  Furthermore, in the upstream gas-liquid separator 14 of the present embodiment, the separated liquid-phase refrigerant is discharged from the liquid-phase refrigerant outlet 14a without accumulating, so the liquid-phase refrigerant separated as the upstream-side gas-liquid separator 14 Refrigerating machine oil in the liquid phase refrigerant that flows into the evaporator 16 by the refrigerating machine oil dissolved in the liquid phase refrigerant stored in the upstream side gas-liquid separator 14 as in the case where a gas-liquid separator having a function of storing the gas is employed. There is no change in concentration.

  Furthermore, since the downstream gas-liquid separator 17 of the present embodiment has a function of storing the separated liquid-phase refrigerant, the gas-phase refrigerant can be reliably supplied to the suction port side of the compressor 11. The problem of liquid compression of the compressor 11 can be avoided. Furthermore, by returning a part of the liquid-phase refrigerant in which the refrigeration oil stored in the downstream gas-liquid separator 17 is melted to the gas-phase refrigerant on the inlet side of the compressor 11 through the oil return passage 17a, Lubrication failure of the compressor 11 can be suppressed.

  Further, according to the ejector refrigeration cycle 10 of the present embodiment, since the high-pressure refrigerant passage 18 as the internal heat exchange means is provided, the liquid-phase refrigerant in the downstream gas-liquid separator 17 is vaporized, and the liquid phase The concentration of the refrigeration oil in the refrigerant can be increased. Therefore, the refrigerant in which the refrigerating machine oil is dissolved at a high concentration can be returned to the gas-phase refrigerant on the suction port side of the compressor 11, and poor lubrication of the compressor 11 can be effectively suppressed.

(Second Embodiment)
In the ejector refrigeration cycle 10 of the present embodiment, an example in which the configuration of the refrigerating machine oil concentration adjusting means is changed with respect to the first embodiment as shown in the overall configuration diagram of FIG. 3 will be described. The refrigerating machine oil concentration adjusting means of this embodiment uses the oil return hole 14c formed in the bottom surface of the downstream gas-liquid separator 17 and the refrigerating machine oil in the upstream gas-liquid separator 14 to the refrigerant flow downstream of the mixed phase refrigerant outlet 14b. It is comprised by the refrigerator oil bypass passage 23a guide | induced to the side.

  Note that the refrigeration oil in the upstream gas-liquid separator 14 includes both the refrigeration oil dissolved in the refrigerant in the upstream gas-liquid separator 14 and the refrigeration oil deposited from the refrigerant in the upstream gas-liquid separator 14. Is included. Moreover, in FIG. 3, the same code | symbol is attached | subjected to the same or equivalent part as 1st Embodiment. The same applies to the following drawings.

  Specifically, the refrigerating machine oil bypass passage 23a of the present embodiment is constituted by a refrigerant pipe that connects the oil return hole 14c and the downstream gas-liquid separator 17, and the refrigerating machine oil that flows out of the oil return hole 14c or The refrigerant in which the refrigerating machine oil is dissolved at a high concentration is introduced into the downstream gas-liquid separator 17. Other configurations are the same as those of the first embodiment.

  Therefore, when the ejector refrigeration cycle 10 of this embodiment is operated, the same effect as that of the first embodiment can be obtained. That is, according to the ejector refrigeration cycle 10 of the present embodiment, the concentration of the refrigeration oil in the liquid refrigerant flowing out from the liquid refrigerant outlet 14a of the upstream gas-liquid separator 14 can be adjusted to an appropriate concentration. The cooling capacity in the evaporator 16 can be brought close to the maximum value.

  This will be explained in more detail. In a centrifugal gas-liquid separator such as the upstream gas-liquid separator 14 of this embodiment, the distribution of the refrigeration oil concentration in the liquid-phase refrigerant is distributed by the action of centrifugal force. Can be generated. For example, as in this embodiment, if a refrigeration oil whose density is smaller than the density of the liquid refrigerant is adopted, the concentration of the refrigeration oil in the liquid refrigerant on the swivel center side is set to the liquid refrigerant on the outer peripheral side. The concentration of the refrigerating machine oil in can be higher.

  Therefore, by adjusting the position where the oil return hole 14c is provided and the opening shape of the oil return hole 14c, the concentration of the refrigerating machine oil in the liquid phase refrigerant guided into the downstream gas-liquid separator 17 can be adjusted. Further, by adjusting the concentration of the refrigeration oil in the liquid phase refrigerant led to the downstream gas-liquid separator 17 in this way, the liquid phase refrigerant flowing out from the liquid phase refrigerant outlet 14a of the upstream gas-liquid separator 14 is adjusted. The concentration of refrigerating machine oil can be adjusted.

  Therefore, in the present embodiment, the upstream side gas-liquid is set by appropriately setting the inner diameter (refrigerant passage area) of the refrigerating machine oil bypass passage 23a constituting the refrigerating machine oil concentration adjusting means or the arrangement and opening shape of the oil return hole 14c. The concentration of the refrigeration oil in the liquid phase refrigerant flowing out from the liquid phase refrigerant outlet 14a of the separator 14 is adjusted so that the cooling capacity in the evaporator 16 approaches the maximum value.

(Third embodiment)
In the ejector-type refrigeration cycle 10 of the present embodiment, as shown in the overall configuration diagram of FIG. 4, the ejector 20 and the upstream gas-liquid separator 14 are eliminated from the second embodiment, and the gas-liquid separation means is unified. An example in which the body-shaped ejector 25 is employed will be described.

  The ejector 25 of the present embodiment not only functions as a refrigerant decompression unit and a refrigerant circulation unit (refrigerant transport unit), but also functions as a gas-liquid separation unit that separates the gas-liquid of the decompressed refrigerant. That is, the ejector 25 of the present embodiment exhibits a function equivalent to that of the ejector 20 and the upstream gas-liquid separator 14 described in the second embodiment integrally formed.

  A specific configuration of the ejector 25 will be described with reference to FIGS. In addition, the up and down arrows in FIG. 5 indicate the up and down directions in a state where the ejector refrigeration cycle 10 is mounted on the vehicle air conditioner. FIG. 6 is a schematic cross-sectional view for explaining the function of each refrigerant passage of the ejector 25, and the same reference numerals are given to the portions that perform the same functions as those in FIG.

  First, as shown in FIG. 5, the ejector 25 of this embodiment includes a body 30 configured by combining a plurality of constituent members. Specifically, the body 30 includes a housing body 31 that is formed of a prismatic or cylindrical metal or resin and forms an outer shell of the ejector 25, and a nozzle body 32 is provided in the housing body 31. The middle body 33, the lower body 34, etc. are fixed.

  The housing body 31 includes a refrigerant inlet 31 a for allowing refrigerant flowing out of the radiator 12 to flow into the interior, a refrigerant suction port 31 b for sucking refrigerant flowing out of the evaporator 16, and an upstream gas-liquid formed inside the body 30. A liquid-phase refrigerant outlet 31c that causes the liquid-phase refrigerant separated in the separation space 30f to flow out to the refrigerant inlet side of the evaporator 16, and a low-pressure refrigerant outlet that causes the low-pressure refrigerant to flow out to the inlet side of the downstream gas-liquid separator 17. 31d and the like are formed.

  The nozzle body 32 is formed of a substantially conical metal member or the like that tapers in the refrigerant flow direction, and is press-fitted into the housing body 31 such that the axial direction is parallel to the vertical direction (vertical direction in FIG. 5). It is fixed by means of Between the upper side of the nozzle body 32 and the housing body 31, a swirling space 30a for swirling the refrigerant flowing from the refrigerant inlet 31a is formed.

  The swirling space 30a is formed in a rotating body shape, and the central axis shown by the one-dot chain line in FIG. 5 extends in the vertical direction. The rotating body shape is a three-dimensional shape formed when a plane figure is rotated around one straight line (central axis) on the same plane. More specifically, the swirl space 30a of the present embodiment is formed in a substantially cylindrical shape. Of course, you may form in the shape etc. which combined the cone or the truncated cone, and the cylinder.

  Furthermore, the refrigerant inflow passage 31e that connects the refrigerant inlet 31a and the swirling space 30a extends in the tangential direction of the inner wall surface of the swirling space 30a when viewed from the central axis direction of the swirling space 30a. Thereby, the refrigerant that has flowed into the swirl space 30a from the refrigerant inflow passage 31e flows along the inner wall surface of the swirl space 30a and swirls in the swirl space 30a.

  The refrigerant inflow passage 31e does not need to be formed so as to completely coincide with the tangential direction of the swirl space 30a when viewed from the central axis direction of the swirl space 30a, and at least in the tangential direction of the swirl space 30a. As long as a component is included, it may be formed including a component in another direction (for example, a component in the axial direction of the swirling space 30a).

  Here, since centrifugal force acts on the refrigerant swirling in the swirling space 30a, the refrigerant pressure on the central axis side is lower than the refrigerant pressure on the outer peripheral side in the swirling space 30a. Therefore, in the present embodiment, during the normal operation of the ejector refrigeration cycle 10, the refrigerant pressure on the central axis side in the swirling space 30a is reduced to a pressure at which the refrigerant boils under reduced pressure (causes cavitation).

  Such adjustment of the refrigerant pressure on the central axis side in the swirling space 30a can be realized by adjusting the swirling flow velocity of the refrigerant swirling in the swirling space 30a. Further, the swirl flow rate can be adjusted by adjusting the area ratio between the passage sectional area of the refrigerant inflow passage 31e and the vertical sectional area in the axial direction of the swirling space 30a, for example. Note that the swirling flow velocity in the present embodiment means the flow velocity in the swirling direction of the refrigerant in the vicinity of the outermost peripheral portion of the swirling space 30a.

  Further, in the nozzle body 32, a decompression space 30b is formed in which the refrigerant that has flowed out of the swirl space 30a is decompressed and flows out downstream. The decompression space 30b is formed in a rotating body shape in which a cylindrical space and a frustoconical space that continuously spreads from the lower side of the cylindrical space and gradually expands in the refrigerant flow direction. The central axis of the working space 30b is arranged coaxially with the central axis of the swirling space 30a.

  Further, inside the decompression space 30b, there is formed a minimum passage area portion 30m having the smallest refrigerant passage area in the decompression space 30b, and a passage forming member 35 that changes the passage area of the minimum passage area portion 30m. Has been placed. The passage forming member 35 is formed in a substantially conical shape that gradually expands toward the downstream side of the refrigerant flow, and the central axis thereof is arranged coaxially with the central axis of the decompression space 30b. In other words, the passage forming member 35 is formed in a conical shape whose cross-sectional area increases as the distance from the decompression space 30b increases.

  As the refrigerant passage formed between the inner peripheral surface of the portion forming the pressure reducing space 30b of the nozzle body 32 and the outer peripheral surface on the upper side of the passage forming member 35, as shown in FIG. The tip 131 is formed on the upstream side of the refrigerant flow from the portion 30m and gradually decreases in the refrigerant passage area until reaching the minimum passage area 30m, and the refrigerant passage is formed on the downstream side of the refrigerant flow from the minimum passage area 30m. A divergent portion 132 whose area gradually increases is formed.

  At the downstream side and the divergent portion 132 of the tapered portion 131, the decompression space 30b and the passage forming member 35 are overlapped (overlapped) when viewed from the radial direction, so the shape of the axial cross section of the refrigerant passage is circular. It becomes an annular shape (a donut shape excluding a small-diameter circular shape arranged coaxially from a large-diameter circular shape).

  Further, in the present embodiment, the inner peripheral surface of the portion forming the pressure reducing space 30b of the nozzle body 32 and the passage forming member 35 so that the refrigerant passage area in the divergent portion 132 gradually increases toward the downstream side of the refrigerant flow. The outer peripheral surface is formed.

  In the present embodiment, the refrigerant passage formed between the inner peripheral surface of the pressure reducing space 30b and the outer peripheral surface on the top side of the passage forming member 35 by this passage shape is the first embodiment as shown in FIG. The nozzle passage 13a functions in the same manner as the refrigerant passage formed in the nozzle portion 21 described in the above. Further, in the nozzle passage 13a, the refrigerant is decompressed, and the flow rate of the refrigerant in the gas-liquid two-phase state is increased so as to be higher than the two-phase sound velocity, and is injected.

  Note that the refrigerant passage formed between the inner peripheral surface of the decompression space 30b and the outer peripheral surface on the top side of the passage forming member 35 in this embodiment is the outer periphery of the passage forming member 35 as shown in FIG. This is a refrigerant passage formed so as to include a range where a line segment extending in the normal direction from the surface intersects a portion of the nozzle body 32 forming the decompression space 30b.

  Further, since the refrigerant flowing into the nozzle passage 13a swirls in the swirling space 30a, the refrigerant flowing through the nozzle passage 13a and the jet refrigerant injected from the nozzle passage 13a are the same as the refrigerant swirling in the swirling space 30a. It has a velocity component in the direction of turning in the direction.

  Next, the middle body 33 shown in FIG. 5 is provided with a rotating body-shaped through hole penetrating the front and back at the center, and a driving means 37 for displacing the passage forming member 35 on the outer peripheral side of the through hole. It is formed of a housed metal disk-shaped member. The central axis of the through hole of the middle body 33 is arranged coaxially with the central axes of the swirl space 30a and the decompression space 30b. The middle body 33 is fixed inside the housing body 31 and below the nozzle body 32 by means such as press fitting.

  Furthermore, an inflow space 30c is formed between the upper surface of the middle body 33 and the inner wall surface of the housing body 31 facing the middle body 33 for retaining the refrigerant flowing in from the refrigerant suction port 31b. In the present embodiment, since the tapered tip portion on the lower side of the nozzle body 32 is positioned inside the through hole of the middle body 33, the inflow space 30c has a cross section when viewed from the central axis direction of the swirl space 30a and the decompression space 30b. It is formed in an annular shape.

  The suction refrigerant inflow passage connecting the refrigerant suction port 31b and the inflow space 30c extends in the tangential direction of the inner peripheral wall surface of the inflow space 30c when viewed from the central axis direction of the inflow space 30c. Thus, in the present embodiment, the refrigerant that has flowed into the inflow space 30c from the refrigerant suction port 31b via the suction refrigerant inflow passage is swirled in the same direction as the refrigerant in the swirling space 30a.

  Further, in the range where the lower side of the nozzle body 32 is inserted, that is, in the range where the middle body 33 and the nozzle body 32 overlap when viewed from the radial direction perpendicular to the axis among the through holes of the middle body 33, the tapered tip of the nozzle body 32 is formed. The refrigerant passage area gradually decreases in the refrigerant flow direction so as to conform to the outer peripheral shape.

  As a result, a suction passage 30d is formed between the inner peripheral surface of the through hole and the outer peripheral surface of the tapered tip portion on the lower side of the nozzle body 32 to communicate the inflow space 30c and the downstream side of the refrigerant flow in the decompression space 30b. Is done. That is, in this embodiment, the suction passage 13b for sucking the refrigerant from the outside is formed by the suction refrigerant inflow passage connecting the refrigerant suction port 31b and the inflow space 30c, the inflow space 30c, and the suction passage 30d.

  The cross section of the suction passage 30d perpendicular to the central axis is also formed in an annular shape, and the refrigerant flowing through the suction passage 30d also has a speed component in the direction swirling in the same direction as the refrigerant swirling in the swirling space 30a. Further, the refrigerant outlet of the suction passage 13b (specifically, the refrigerant outlet of the suction passage 30d) opens in an annular shape on the outer peripheral side of the refrigerant outlet (refrigerant injection port) of the nozzle passage 13a.

  Further, in the through hole of the middle body 33, a pressure increasing space 30e formed in a substantially truncated cone shape gradually spreading in the refrigerant flow direction is formed on the downstream side of the refrigerant flow in the suction passage 30d. The pressurizing space 30e is a space into which the injection refrigerant injected from the pressure reducing space 30b (specifically, the nozzle passage 13a) and the suction refrigerant sucked from the suction passage 13b flow.

  A lower portion of the above-described passage forming member 35 is disposed inside the pressure increasing space 30e. Further, the expansion angle of the conical side surface of the passage forming member 35 in the pressure increasing space 30e is smaller than the expansion angle of the frustoconical space of the pressure increasing space 30e. The flow gradually expands toward the downstream side.

  In the present embodiment, by expanding the refrigerant passage area in this way, as shown in FIG. 6, the inner peripheral surface of the middle body 33 forming the pressurizing space 30 e and the outer peripheral surface on the lower side of the passage forming member 35 are formed. The refrigerant passage formed therebetween is a diffuser passage 13c that functions in the same manner as the diffuser portion 22b described in the first embodiment. Then, the kinetic energy of the mixed refrigerant of the injected refrigerant and the suction refrigerant is converted into pressure energy in the diffuser passage 13c.

  Further, the axial vertical cross-sectional shape of the diffuser passage 13c is also formed in an annular shape, and the refrigerant flowing through the diffuser passage 13c is also from the speed component in the swirling direction of the injection refrigerant injected from the nozzle passage 13a and the suction passage 13b. The speed component in the swirling direction of the sucked suction refrigerant has a speed component in the direction swirling in the same direction as the refrigerant swirling in the swirling space 30a.

  Next, the drive means 37 which is disposed inside the middle body 33 and displaces the passage forming member 35 will be described. The driving means 37 is configured to have a circular thin plate-like diaphragm 37a which is a pressure responsive member. More specifically, as shown in FIG. 5, the diaphragm 37a is fixed by means such as welding so as to partition a columnar space formed on the outer peripheral side of the middle body 33 into two upper and lower spaces.

  Of the two spaces partitioned by the diaphragm 37a, the upper space (the inflow space 30c side) constitutes an enclosed space 37b in which a temperature-sensitive medium that changes in pressure according to the temperature of the refrigerant flowing out of the evaporator 16 is enclosed. Yes. A temperature sensitive medium having the same composition as the refrigerant circulating in the ejector refrigeration cycle 10 is enclosed in the enclosed space 37b so as to have a predetermined density. Therefore, the temperature sensitive medium in this embodiment is R134a.

  On the other hand, the lower space of the two spaces partitioned by the diaphragm 37a constitutes an introduction space 37c for introducing the refrigerant flowing out of the evaporator 16 through a communication path (not shown). Therefore, the temperature of the refrigerant flowing out of the evaporator 16 is transmitted to the temperature-sensitive medium enclosed in the enclosed space 37b through the lid member 37d and the diaphragm 37a that partition the inflow space 30c and the enclosed space 37b.

  Here, as is apparent from FIGS. 5 and 6, the suction passage 13 b is disposed above the middle body 33 of the present embodiment, and the diffuser passage 13 c is disposed below the middle body 33. Accordingly, at least a part of the driving means 37 is disposed at a position sandwiched between the suction passage 13b and the diffuser passage 13c when viewed from the radial direction of the central axis.

  More specifically, the enclosed space 37b of the driving means 37 is a position where it overlaps with the suction passage 13b and the diffuser passage 13c when viewed from the central axis direction of the swivel space 30a, the passage forming member 35, etc. It arrange | positions in the position enclosed by the channel | path 13b for diffusers, and the diffuser channel | path 13c. As a result, the temperature of the refrigerant flowing out of the evaporator 16 is transmitted to the enclosed space 37b, and the internal pressure of the enclosed space 37b becomes a pressure corresponding to the temperature of the refrigerant flowing out of the evaporator 16.

  Further, the diaphragm 37a is deformed according to a differential pressure between the internal pressure of the enclosed space 37b and the pressure of the refrigerant flowing out of the evaporator 16 flowing into the introduction space 37c. For this reason, the diaphragm 37a is preferably formed of a tough material having high elasticity and good heat conduction, and is preferably formed of a thin metal plate such as stainless steel (SUS304).

  Further, the upper end side of a columnar operating rod 37e is joined to the center of the diaphragm 37a by means such as welding, and the outer peripheral side of the lowermost side (bottom) of the passage forming member 35 is fixed to the lower end side of the operating rod 37e. Has been. Thereby, the diaphragm 37a and the passage forming member 35 are connected, and the passage forming member 35 is displaced in accordance with the displacement of the diaphragm 37a, and the refrigerant passage area of the nozzle passage 13a (passage sectional area in the minimum passage area portion 30m) is adjusted. The

  Specifically, when the temperature (superheat degree) of the refrigerant flowing out of the evaporator 16 increases, the saturation pressure of the temperature-sensitive medium enclosed in the enclosed space 37b increases, and the pressure in the introduction space 37c is subtracted from the internal pressure of the enclosed space 37b. Increased differential pressure. Thereby, the diaphragm 37a displaces the channel | path formation member 35 in the direction (vertical direction lower side) which enlarges the channel | path cross-sectional area in the minimum channel | path area part 30m.

  On the other hand, when the temperature (superheat degree) of the refrigerant flowing out of the evaporator 16 is lowered, the saturation pressure of the temperature sensitive medium enclosed in the enclosed space 37b is lowered, and the difference obtained by subtracting the pressure of the introduction space 37c from the internal pressure of the enclosed space 37b. The pressure is reduced. Thereby, the diaphragm 37a displaces the passage forming member 35 in a direction (vertical direction upper side) in which the passage sectional area in the minimum passage area portion 30m is reduced.

  Thus, the diaphragm 37a displaces the passage forming member 35 in the vertical direction according to the degree of superheat of the refrigerant flowing out of the evaporator 16, so that the degree of superheat of the refrigerant flowing out of the evaporator 16 approaches a predetermined value. The passage sectional area in the minimum passage area portion 30m can be adjusted. The gap between the operating rod 37e and the middle body 33 is sealed by a sealing member such as an O-ring (not shown), and the refrigerant does not leak from the gap even if the operating rod 37e is displaced.

  Further, the bottom surface of the passage forming member 35 receives a load of a coil spring 40 fixed to the lower body 34. The coil spring 40 applies a load that urges the passage forming member 35 to the side (the upper side in FIG. 5) that reduces the passage cross-sectional area in the minimum passage area 30m, and adjusts this load. It is also possible to change the valve opening pressure of the passage forming member 35 to change the target degree of superheat.

  Further, in the present embodiment, a plurality of (specifically, two) cylindrical spaces are provided on the outer peripheral side of the middle body 33, and a circular thin plate-like diaphragm 37a is fixed inside each of these spaces to drive two drives. Although the means 37 is comprised, the number of the drive means 37 is not limited to this. In addition, when providing the drive means 37 in multiple places, it is desirable to arrange | position at equal angle intervals with respect to a central axis, respectively.

  Alternatively, a diaphragm formed by an annular thin plate may be fixed in a space formed in an annular shape when viewed from the axial direction, and the diaphragm and the passage forming member 35 may be connected by a plurality of operating rods. Good.

  Next, the lower body 34 is formed of a cylindrical metal member or the like, and is fixed by means such as press fitting or screwing so as to close the bottom surface side of the housing body 31. In the internal space of the housing body 31, an upstream gas-liquid separation space 30f is formed between the upper surface side of the lower body 34 and the bottom surface side of the middle body 33 to separate the gas and liquid of the refrigerant flowing out from the diffuser passage 13c. Has been.

  The upstream gas-liquid separation space 30f is formed as a substantially cylindrical rotating body-shaped space, and the central axis of the upstream gas-liquid separation space 30f is also a swirl space 30a, a decompression space 30b, and a passage forming member. It is arranged coaxially with a central axis such as 35.

  Further, the refrigerant flowing out of the diffuser passage 13c and flowing into the upstream gas-liquid separation space 30f has a velocity component in a direction swirling in the same direction as the refrigerant swirling in the swirling space 30a. Accordingly, the upstream-side gas-liquid separation space 30f is a centrifugal-type gas-liquid separation means that separates the gas-liquid of the refrigerant by the action of centrifugal force, like the upstream-side gas-liquid separator 14 described in the first embodiment. Function as.

  In addition, the internal volume of the upstream gas-liquid separation space 30f is formed to be approximately the same as that of the upstream gas-liquid separator 14 described in the first embodiment. Therefore, in the upstream gas-liquid separation space 30f, the separated liquid-phase refrigerant is allowed to flow out from the liquid-phase refrigerant outlet 31c without accumulating, and the remaining refrigerant that could not be allowed to flow out from the liquid-phase refrigerant outlet 31c is mixed-phased. The refrigerant flows out from the refrigerant outlet 34d.

  The mixed phase refrigerant outlet 34 d is formed at the upper end of a cylindrical pipe portion 34 a provided at the center of the lower body 34. The pipe portion 34a is disposed coaxially with the upstream gas-liquid separation space 30f and extends upward. Therefore, the liquid refrigerant separated in the upstream gas-liquid separation space 30f temporarily stays on the outer peripheral side of the pipe portion 34a and flows out from the liquid refrigerant outlet 31c.

  Also, a mixed phase refrigerant outflow passage 34b is formed in the pipe portion 34a to guide the gas phase refrigerant flowing into the mixed phase refrigerant outlet 34d or the refrigerant in which the gas phase refrigerant and the liquid phase mixture are mixed into the low pressure refrigerant outlet 31d. ing. Further, the above-described coil spring 40 is fixed to the upper end portion of the pipe portion 34a. The coil spring 40 also functions as a vibration buffer member that attenuates the vibration of the passage forming member 35 caused by pressure pulsation when the refrigerant is depressurized.

  In addition, the refrigeration oil in the upstream gas-liquid separation space 30f is led to the root part (lowermost part) of the pipe part 34a into the mixed-phase refrigerant outflow passage 34b on the downstream side of the mixed-phase refrigerant outlet 34d. Thus, a refrigerating machine oil bypass passage 34c for adjusting the concentration of refrigerating machine oil in the liquid phase refrigerant flowing out from the liquid phase refrigerant outlet 31c is formed.

  The refrigerating machine oil in the upstream gas-liquid separation space 30f is the same as in the second embodiment, the refrigerating machine oil dissolved in the refrigerant in the upstream gas-liquid separation space 30f and the upstream gas-liquid separation space 30f. Both refrigeration oil precipitated from the refrigerant are included. Other configurations are the same as those of the second embodiment.

  As described above, the ejector 25 of this embodiment exhibits the same function as that of the ejector 20 and the upstream gas-liquid separator 14 described in the second embodiment, and therefore the ejector of this embodiment. When the refrigeration cycle 10 is operated, the same effect as in the second embodiment can be obtained.

  That is, according to the ejector 25 of the present embodiment, similarly to the second embodiment, the inner diameter (refrigerant passage area) of the refrigeration oil bypass passage 34c or the arrangement and opening shape of the refrigeration oil bypass passage 34c are appropriately set. Thus, the concentration of the refrigerating machine oil in the liquid phase refrigerant flowing out from the liquid phase refrigerant outlet 31c can be adjusted to an appropriate concentration. And the cooling capacity in the evaporator 16 can be approximated to the maximum value.

  Further, according to the ejector 25 of the present embodiment, by turning the refrigerant in the swirl space 30a, the refrigerant pressure on the swivel center side in the swirl space 30a is reduced to the pressure that becomes the saturated liquid phase refrigerant or the refrigerant is reduced. The pressure can be reduced to boiling (causing cavitation). Thus, the gas phase refrigerant is present in the swirl space 30a in the vicinity of the swirl center line, and the liquid single phase is surrounded by the two-phase separation so that a larger amount of gas-phase refrigerant exists on the inner periphery side than the outer periphery side of the swirl center shaft. State.

  As the refrigerant in the two-phase separation state flows into the nozzle passage 13a in this manner, the tip 131 of the nozzle passage 13a has a wall surface boiling that occurs when the refrigerant is separated from the outer peripheral side wall surface of the annular refrigerant passage. Boiling of the refrigerant is promoted by interfacial boiling by boiling nuclei generated by cavitation of the refrigerant on the central axis side of the annular refrigerant passage. As a result, the refrigerant flowing into the minimum passage area 30m of the nozzle passage 13a approaches a gas-liquid mixed state in which the gas phase and the liquid phase are uniformly mixed.

  Then, the flow of refrigerant in the gas-liquid mixed state is choked in the vicinity of the minimum passage area portion 30m, and the gas-liquid mixed state refrigerant that has reached the speed of sound by this choking is accelerated by the divergent portion 132 and injected. The Thus, by promoting boiling by both wall boiling and interfacial boiling, the gas-liquid mixed refrigerant can be efficiently accelerated until it reaches the speed of sound, so that the energy conversion efficiency in the nozzle passage 13a (corresponding to the nozzle efficiency of the prior art) is increased. Can be improved.

  In addition, the body 30 of the ejector 25 of the present embodiment is formed with an upstream gas-liquid separation space 30f for separating the gas-liquid refrigerant flowing out of the diffuser passage 13c, so that the gas-liquid separation means is separate from the ejector 25. The volume of the upstream side gas-liquid separation space 30f can be effectively reduced as compared with the case where the above is provided.

  In other words, in the upstream gas-liquid separation space 30f of the present embodiment, the refrigerant flowing out of the diffuser passage 13c formed in an annular cross section already has a velocity component in the swirling direction, so the upstream gas-liquid separation space 30f Therefore, it is not necessary to provide a space for generating a swirling flow of the refrigerant. Accordingly, the volume of the upstream gas-liquid separation space 30f can be effectively reduced as compared with the case where the gas-liquid separation means is provided separately from the ejector 25.

(Fourth embodiment)
In the present embodiment, as shown in FIG. 7, an example in which the configuration of the ejector 25 is changed with respect to the third embodiment will be described. Specifically, in the ejector 25 of the present embodiment, a refrigerator oil bypass passage 35 b is connected to the center of the bottom surface of the passage forming member 35.

  The refrigerating machine oil bypass passage 35b of the present embodiment is constituted by a pipe-shaped member that guides the refrigerating machine oil in the diffuser passage 13c to the downstream side of the refrigerant flow of the mixed-phase refrigerant outlet 34d, and the mixed-phase refrigerant flows out from the bottom surface of the passage forming member 35. It extends downward into the passage 34b. Therefore, the refrigerating machine oil bypass passage 35 b is displaced together with the passage forming member 35.

  The refrigerating machine oil in the diffuser passage 13c includes both refrigerating machine oil dissolved in the refrigerant flowing through the diffuser passage 13c and refrigerating machine oil deposited from the refrigerant flowing through the diffuser passage 13c.

  Further, the passage forming member 35 of the present embodiment is formed with a small diameter hole 35a through which the refrigerating machine oil in the diffuser passage 13c flows out. More specifically, the inlet portion of the small-diameter hole 35a is formed in a portion of the passage forming member 35 that forms the diffuser passage 13c and closer to the outlet side than the inlet side of the diffuser passage 13c. The outlet portion of the small diameter hole 35 a is open at the center of the bottom surface of the passage forming member 35.

  Thereby, in the refrigerating machine oil bypass passage 35b of the present embodiment, the refrigerating machine oil flowing out from the small-diameter hole 35a or the refrigerant in which the refrigerating machine oil is melted at a high concentration becomes a mixed phase refrigerant outflow path 34b on the downstream side of the refrigerant flow of the mixed phase refrigerant outlet 34d. Leads in. Other configurations are the same as those of the third embodiment.

  Therefore, when the ejector refrigeration cycle 10 of the present embodiment is operated, the same effect as that of the first embodiment can be obtained.

  That is, according to the ejector 25 of the present embodiment, as in the first embodiment, by setting the inner diameter (refrigerant passage area) of the refrigerating machine oil bypass passage 35b or the diameter of the small diameter hole 35a to an appropriate value, The concentration of the refrigerating machine oil in the liquid phase refrigerant flowing out from the phase refrigerant outlet 31c can be adjusted to an appropriate concentration. And it adjusts so that the cooling capacity in the evaporator 16 may approach the maximum value.

  Furthermore, according to the ejector 25 of the present embodiment, as in the third embodiment, the energy conversion efficiency (corresponding to the nozzle efficiency of the prior art) in the nozzle passage 13a can be improved, and the upstream gas-liquid separation space 30f. Can be effectively reduced in volume.

(Fifth embodiment)
In the ejector refrigeration cycle 10 of the present embodiment, as shown in the overall configuration diagram of FIG. 8, the high-pressure refrigerant passage 18 and the downstream gas-liquid separator 17 are abolished as compared with the third embodiment, and the ejector 25 An example in which the configuration is changed will be described.

  Specifically, in the ejector 25 of the present embodiment, the partition plate 38 is disposed inside the mixed phase refrigerant outflow passage 34b, so that the gas phase refrigerant and liquid phase flowing out from the mixed phase refrigerant outlet 34d are disposed inside the ejector 25. 30 g of downstream gas-liquid separation spaces which isolate | separate the gas-liquid of the refrigerant | coolant with which the refrigerant | coolant was mixed and store the isolate | separated liquid phase refrigerant | coolant are formed.

  The partition plate 38 is formed of a plate-like member that spreads from the lower side to the upper side, and in the downstream gas-liquid separation space 30g, the refrigerant flowing through the interior collides with the partition plate 38 and has a high density liquid phase refrigerant. Is dropped downward to constitute a gravity drop type gas-liquid separation means for separating the gas-liquid of the refrigerant. Therefore, the downstream gas-liquid separation space 30g of the present embodiment performs the same function as the downstream gas-liquid separator 17 described in the first embodiment.

  In addition, a gas phase refrigerant outflow passage is formed on the upper side of the partition plate 38 through which the gas phase refrigerant separated in the downstream gas-liquid separation space 30g flows out to the low pressure refrigerant outlet 31d side. Further, on the lower side of the partition plate 38, refrigeration oil that penetrates the front and back of the partition plate 38 and is dissolved in the liquid-phase refrigerant stored in the downstream gas-liquid separation space 30 g is supplied to the air on the inlet side of the compressor 11. An oil return hole 38a for returning to the phase refrigerant is formed.

  Therefore, when the ejector refrigeration cycle 10 of the present embodiment is operated, the effect of increasing the concentration of the refrigeration oil in the liquid refrigerant in the downstream gas-liquid separation space 30g by providing the internal heat exchange means cannot be obtained. The effect similar to 1st Embodiment can be acquired.

  That is, according to the ejector 25 of the present embodiment, the concentration of the refrigeration oil in the liquid phase refrigerant flowing out from the liquid phase refrigerant outlet 31c can be adjusted to an appropriate concentration as in the third embodiment, and the evaporator The cooling capacity at 16 can be brought close to the maximum value.

  Further, in the present embodiment, the downstream gas-liquid separator 17 described in the first embodiment is abolished, and the downstream gas-liquid separation space 30g is formed inside the ejector 25. Therefore, the ejector refrigeration cycle 10 The overall size can be reduced.

(Sixth embodiment)
In the ejector refrigeration cycle 10 of the present embodiment, as shown in the overall configuration diagram of FIG. 9, an example in which the downstream gas-liquid separator 17 is abolished and the configuration of the ejector 25 is changed with respect to the third embodiment. Will be explained.

  In the ejector 25 of the present embodiment, a bottomed cylindrical cup-shaped member 39 is provided on the lower side, and a gas-phase refrigerant and a liquid-phase refrigerant flowing out from the mixed-phase refrigerant outlet 34d are mixed in the cup-shaped member 39. A gas-liquid separation space 30g for separating the gas-liquid refrigerant and storing the separated liquid-phase refrigerant is formed.

  Furthermore, the low-pressure refrigerant outlet 31d of the present embodiment is formed in the most downstream part of the refrigerant flow of the gas-phase refrigerant outflow pipe 41 that causes the gas-phase refrigerant separated in the downstream gas-liquid separation space 30g to flow out. In addition, a high-pressure refrigerant passage 18 equivalent to that of the first embodiment is disposed inside the liquid-phase refrigerant stored in the downstream gas-liquid separation space 30g, and the first surface of the cup-shaped member 39 of the ejector 25 has a first An oil return passage 17a similar to the embodiment is connected.

  Other configurations are the same as those of the first embodiment. Therefore, when the ejector refrigeration cycle 10 of the present embodiment is operated, the same effect as that of the first embodiment can be obtained.

  That is, according to the ejector 25 of the present embodiment, the concentration of the refrigeration oil in the liquid phase refrigerant flowing out from the liquid phase refrigerant outlet 31c can be adjusted to an appropriate concentration as in the third embodiment, and the evaporator The cooling capacity at 16 can be brought close to the maximum value. Furthermore, as in the fifth embodiment, the ejector refrigeration cycle 10 as a whole can be reduced in size.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention. In addition, the means disclosed in each of the above-described embodiments may be appropriately combined within a practicable range.

  (1) In the first and second embodiments described above, an example in which the refrigerating machine oil concentration adjusting means is configured by the refrigerating machine oil bypass passages 23 and 23a formed by a refrigerant pipe having a small diameter with respect to the other refrigerant pipes will be described. However, the refrigerator oil concentration adjusting means is not limited to this. For example, a refrigerant pipe having the same diameter as other refrigerant pipes may be adopted, and a flow rate adjusting valve or the like may be disposed on the refrigerant pipe to constitute the refrigerator oil concentration adjusting means.

  In the above-described embodiment, for example, the liquid-phase refrigerant that flows into the evaporator 16 by setting the inner diameter of the refrigerator oil bypass passage 23 or the diameter of the small-diameter hole 22c formed in the body portion 22 to an appropriate value. Although the example which adjusted the density | concentration of the refrigerating machine oil in was demonstrated, adjustment of the density | concentration of refrigerating machine oil is not limited to this.

  For example, the concentration of the refrigerating machine oil in the liquid phase refrigerant flowing into the evaporator 16 may be adjusted by changing the quantity of the refrigerating machine oil bypass passage 23 and the small diameter hole 22c. This also applies to the refrigerator oil bypass passage 23a and the oil return hole 14c described in the second embodiment, the refrigerator oil bypass passage 34c described in the third embodiment, the small diameter hole 35a described in the fourth embodiment, and the like. It is the same.

  Further, in the third embodiment, the refrigerating machine oil bypass passage 35b is a mixed phase refrigerant that mixes refrigerating machine oil or refrigerating machine oil adhering to the outer peripheral wall surface of the passage forming member 35 that forms the inner circumferential side of the diffuser passage 13c at a high concentration. Although the example provided so that it may guide | lead to the downstream of the outflow port 34d was demonstrated, of course, the refrigerator oil bypass passage 35b is the refrigerator oil or refrigeration adhering to the inner peripheral wall surface of the body 30 which forms the outer peripheral side of the diffuser passage 13c. It may be provided so that the refrigerant in which the machine oil is dissolved at a high concentration is led to the downstream side of the mixed phase refrigerant outlet 34d.

  (2) In the above-described embodiment, by arranging the high-pressure refrigerant passage 18 inside the liquid-phase refrigerant stored in the downstream gas-liquid separator 17 or the downstream gas-liquid separation space 30g as the internal heat exchange means, Although the example which comprised the heat exchange means was demonstrated, an internal heat exchange means is not limited to this.

  For example, if the refrigerant flowing out of the radiator 12 and the liquid-phase refrigerant stored in the downstream gas-liquid separator 17 or the downstream gas-liquid separation space 30g can exchange heat, the downstream gas-liquid separator 17 The internal heat exchange means may be constituted by means for joining the high-pressure refrigerant passage 18 to the outer peripheral side of the cup-shaped member 39 forming the outer peripheral side or downstream side gas-liquid separation space 30g.

  (3) In the ejector 25 of the fifth and sixth embodiments described above, as in the third embodiment, the refrigerator oil bypass that guides the refrigerator oil in the upstream gas-liquid separation space 30f to the downstream side of the mixed-phase refrigerant outlet 34d. Although the passage formed with the passage 34c is adopted, the refrigerating machine oil bypass passage 35b for guiding the refrigerating machine oil in the diffuser passage 13c to the downstream side of the mixed phase refrigerant outlet 34d is formed as in the fourth embodiment. May be adopted.

  Further, in the ejector 25 of the third to sixth embodiments, a refrigeration oil bypass passage 34c, a small diameter hole 35a and a refrigeration oil bypass passage 35b are formed, and the refrigeration in the upstream gas-liquid separation space 30f is adopted. Both the machine oil and the refrigeration oil in the diffuser passage 13c may be led to the downstream side of the mixed phase refrigerant outlet 34d.

  (4) In the above-mentioned embodiment, although the example which employ | adopted the subcool type heat exchanger as the heat radiator 12 was demonstrated, you may employ | adopt the normal heat radiator which consists only of the condensation part 12a. Furthermore, you may employ | adopt the liquid receiver (receiver) which isolate | separates the gas-liquid of the refrigerant | coolant thermally radiated with this heat radiator, and stores an excess liquid phase refrigerant with a normal heat radiator.

  Moreover, although the above-mentioned embodiment demonstrated the example which formed structural members, such as the nozzle part 21 and the body part 22 of the ejector 20, and the body 30 and the channel | path formation member 35 of the ejector 25 with each metal, A material will not be limited if the function of a structural member can be exhibited. Therefore, you may form these structural members with resin etc.

  In addition, the ejector 20 of the first and second embodiments described above is not formed with a swirl space that causes a swirl flow in the refrigerant flowing into the nozzle portion 21, but the ejector 25 of the third to sixth embodiments Similarly, you may provide the turning space formation member which forms turning space.

  In the above-described embodiment, the detailed configuration of the downstream gas-liquid separator 17 is not described. However, the downstream gas-liquid separator 17 includes a centrifugal gas-liquid separator and a gravity-fall gas-liquid separator. A separator, a surface tension type gas-liquid separator that performs gas-liquid separation by adhering a liquid-phase refrigerant to an attachment plate bent in a wave shape, and the like may be employed.

  The same applies to the gas-liquid separation means formed by the downstream gas-liquid separation space 30g. Furthermore, the upstream gas-liquid separator 14 and the upstream gas-liquid separation space 30f are not limited to the centrifugal gas-liquid separation means.

  Further, in the above-described third to sixth embodiments, as the driving means 37 for displacing the passage forming member 35, the enclosed space 37b in which the temperature-sensitive medium whose pressure changes with temperature change is enclosed and the feeling in the enclosed space 37b. Although the example which employ | adopted what was comprised with the diaphragm 37a displaced according to the pressure of a thermal medium was demonstrated, a drive means is not limited to this.

  For example, a thermowax that changes in volume depending on temperature may be employed as the temperature-sensitive medium, or a drive unit that includes a shape memory alloy elastic member may be employed. As a means, a member that displaces the passage forming member 35 by an electric mechanism such as an electric motor or a solenoid may be adopted.

  (5) In the above-described embodiment, the example in which the ejector refrigeration cycle 10 according to the present invention is applied to a vehicle air conditioner has been described. However, the application of the ejector refrigeration cycle 10 including the ejector 25 according to the present invention is applied to this. It is not limited. For example, the present invention may be applied to a stationary air conditioner, a cold storage container, a cooling / heating device for a vending machine, and the like.

  Further, in the above-described embodiment, the radiator 12 of the ejector refrigeration cycle 10 according to the present invention is an outdoor heat exchanger that exchanges heat between the refrigerant and the outside air, and the evaporator 16 is used side heat exchange that cools the blown air. In contrast, the evaporator 16 is used as an outdoor heat exchanger that absorbs heat from a heat source such as outside air, and the radiator 12 is used as an indoor heat exchanger that heats a fluid to be heated such as air or water. You may comprise the heat pump cycle to be used.

DESCRIPTION OF SYMBOLS 10 Ejector type refrigeration cycle 11 Compressor 12 Radiator 14, 30f Upstream gas-liquid separator, upstream gas-liquid separation space (upstream gas-liquid separation means)
16 Evaporator 17, 30g Downstream gas-liquid separator, downstream gas-liquid separation space (downstream gas-liquid separation means)
18 High-pressure refrigerant passage (internal heat exchange means)
20, 25 Ejector 23-35b Refrigerator oil bypass passage

Claims (7)

A compressor (11) that compresses and discharges refrigerant mixed with refrigerating machine oil;
A radiator (12) for radiating the refrigerant discharged from the compressor (11);
The refrigerant is sucked from the refrigerant suction port (22a) by the suction action of the high-speed jet refrigerant jetted from the nozzle part (21) for depressurizing the refrigerant flowing out from the radiator (12), and the jet refrigerant and the refrigerant suction An ejector (20) for increasing the pressure of the mixed refrigerant with the suction refrigerant sucked from the port (22a) at the pressure increasing section (22b);
The gas-liquid of the refrigerant flowing out from the ejector (20) is separated, and the separated liquid-phase refrigerant is allowed to flow out from the liquid-phase refrigerant outlet (14a) without accumulating, and the remaining refrigerant is allowed to flow out of the mixed-phase refrigerant outlet (14b). Upstream gas-liquid separation means (14) flowing out from
An evaporator (16) for evaporating the liquid-phase refrigerant flowing out from the liquid-phase refrigerant outlet (14a) and causing the liquid-phase refrigerant to flow out toward the refrigerant suction port (22a);
The gas-liquid of the refrigerant mixed with the gas-phase refrigerant and the liquid-phase refrigerant flowing out from the mixed-phase refrigerant outlet (14b) is separated, and the separated liquid-phase refrigerant is stored and the separated gas-phase refrigerant is stored in the compressor ( 11) a downstream gas-liquid separation means (17) for flowing out to the suction port side;
An ejector type refrigeration cycle comprising: refrigeration oil concentration adjusting means (22c, 23, 14c, 23a) for adjusting the concentration of the refrigeration oil in the liquid phase refrigerant flowing out from the liquid phase refrigerant outlet (14a). .   The refrigerating machine oil concentration adjusting means is constituted by a refrigerating machine oil bypass passage (23) for guiding refrigerating machine oil in the boosting section (22b) to the downstream side of the mixed phase refrigerant outlet (14b). Item 2. An ejector refrigeration cycle according to Item 1. The upstream gas-liquid separation means (14) separates the gas-liquid refrigerant by the action of centrifugal force generated by swirling the refrigerant flowing into the internal space,
The refrigerating machine oil concentration adjusting means is constituted by a refrigerating machine oil bypass passage (23a) for guiding the refrigerating machine oil in the upstream gas-liquid separation means (14) to the downstream side of the mixed-phase refrigerant outlet (14b). The ejector-type refrigeration cycle according to claim 1.   The internal heat exchanging means (18) for exchanging heat between the refrigerant flowing out of the radiator (12) and the liquid phase refrigerant stored in the downstream gas-liquid separation means (17) is provided. 4. The ejector refrigeration cycle according to any one of items 3 to 3. An ejector applied to a vapor compression refrigeration cycle apparatus (10) for circulating a refrigerant mixed with refrigerating machine oil,
A decompression space (30b) that decompresses the refrigerant, a suction passage (13b) that communicates with the downstream side of the refrigerant flow in the decompression space (30b) and sucks the coolant from the outside, and is injected from the decompression space (30b) A body (30) in which a pressurizing space (30e) for allowing the injected refrigerant and the suction refrigerant sucked from the suction passage (13b) to flow in is formed;
At least a portion is disposed in the decompression space (30b) and in the pressurization space (30e), and is formed in a conical shape in which a cross-sectional area increases as the distance from the decompression space (30b) increases. A passage forming member (35) formed,
The refrigerant passage formed between the inner peripheral surface of the body (30) forming the decompression space (30b) and the outer peripheral surface of the passage forming member (35) depressurizes and injects the refrigerant. A nozzle passage (13a) that functions as a nozzle to
A refrigerant passage formed between an inner peripheral surface of a portion of the body (30) forming the pressurizing space (30e) and an outer peripheral surface of the passage forming member (35) includes the injection refrigerant and the suction A diffuser passage (13c) that functions as a diffuser that converts the kinetic energy of the refrigerant mixed with the refrigerant into pressure energy;
In addition, the body (30)
The gas-liquid of the refrigerant flowing out from the diffuser passage (13c) is separated, and the separated liquid-phase refrigerant is discharged to the outside from the liquid-phase refrigerant outlet (31c) without accumulating the separated liquid-phase refrigerant. Upstream gas-liquid separation space (30f) to flow out from the outlet (34d),
And by introducing at least one of the refrigeration oil in the diffuser passage (13c) and the refrigeration oil in the upstream gas-liquid separation space (30f) to the downstream side of the mixed phase refrigerant outlet (34d), Refrigerating machine oil bypass passage (34c, 35b) for adjusting the concentration of the refrigerating machine oil in the liquid phase refrigerant flowing out from the phase refrigerant outlet (31c)
An ejector characterized by being formed.   Further, the body (30) separates the gas-liquid of the refrigerant mixed with the gas-phase refrigerant and the liquid-phase refrigerant flowing out from the mixed-phase refrigerant outlet (34d), and stores the separated liquid-phase refrigerant and stores the separated gas-phase refrigerant. The ejector according to claim 5, wherein a separation space (30 g) is formed.   The internal heat exchanging means (18) for exchanging heat between the refrigerant flowing into the refrigerant inlet (31a) and the liquid phase refrigerant stored in the downstream gas-liquid separation space (30g). The ejector according to 6.

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